Hydroelectric power system and pump

ABSTRACT

A hydroelectric power system and pump suitable for the system are disclosed which can make efficient use of the energy available in water flows with considerably variable flow rates. A simple, compact variable displacement axial piston pump can be operated so as to provide an essentially constant output pumping pressure and variable output volume that varies efficiently in accordance with water flow rate. The system is particularly suitable for shoreline tidal power generation and provides firm power output throughout the tidal slacks occurring during the tidal reversals.

TECHNICAL FIELD

The present disclosure relates to methods and systems for hydroelectricpower generation. In particular, it relates to systems for tidal powergeneration, operation thereof, and to variable displacement, axialpiston pumps suitable for such systems.

BACKGROUND Description of the Related Art

Many coastal locations in the world have the potential for tidal powergeneration but lack the ability to provide firm power. Present tidalpower production designs and systems typically lack the infrastructureor adequate efficiency to store and release a practical amount of energyduring slack tide. For instance, Graham Island of Haida Gwaii ispresently without an adequate firm source of “green” energy to replacethe diesel generators now in use there. Graham Island has the potentialfor both wind and tidal power according to S. Hart, 2008, “HaidaGwaii/Queen Charlotte Islands Demonstration Tidal Power PlantFeasibility Study. A Hatch Energy report for British Columbia Ministryof Energy, Mines and Petroleum Resources.” However, both sources provideintermittent energy production in the absence of storage.

Various systems have been proposed in the art that use water movement asa source of energy and fluid pumped to an elevated reservoir to storethe energy prior to using the fluid to drive a turbine for generatingelectricity. For instance, published US application US2007/258771discloses a simple way using a class #2 simple lever machine principalto harvest and transport energy from the bottom of an ocean or lake fromthe action of water waves beyond the shore and up on land. The fulcrumfor this lever is an anchor on the seafloor, at the opposite end of thislever, the force, or energy, is an attached water container that risesand falls with water wave action. A water pump anchored to the seafloorand reaching the underside of the water container receives the energyand pumps water continually and harmoniously with the vertical movementsof this water container to shore and into a fresh water reservoir. Afterthe water has lost its energy to do work from its loss of elevationbelow the reservoir it can be recycled back to the water pump. Thisapplication will show the water from the reservoir to be used in thegeneration of electricity and either recycled back to the water pump, orwasted after use, and a continual supply of fresh water from anothersource is available for use.

However, the pumps suggested for use in hydroelectric power systems likethe preceding are typically limited in their ability to efficientlyadjust for the variable, intermittent energy available from tides and/orwaves. Pumps considered in the prior art may be unable to both providesufficient output pressure to pump fluid to the reservoir at times ofweak energy supply (e.g. slack tide), while also taking full advantageof the available energy at times of strong energy supply (e.g. peak tideflow rate).

Axial piston pumps using designs and configurations based on rotatingpiston clusters and fixed (non-rotating) swash plates have been used fordecades in diverse high rpm industrial applications (e.g.transmissions). Generally, such pumps are fixed displacement types inwhich the angle of the swash plates with respect to the rotating pistonclusters is fixed. However, axial piston pumps with variabledisplacement are also known in the art in which the angle of the swashplates in the aforementioned designs can be adjusted with respect to therotating piston clusters during use. Further still, fixed displacementaxial piston pumps with fixed piston clusters and swash plates thatrotate at a fixed angle to the shaft are also known in the art.

There remains a continuing need for more efficient hydroelectric powersystems and pumps therefor to store and release energy from watersources flowing at considerably varied speeds. The present disclosureaddresses this need while additionally providing other benefits asdisclosed herein.

BRIEF SUMMARY

A hydroelectric power system is disclosed in which a waterwheel drives avariable displacement piston pump via swash plates. The swash plate isangled to meet minimum water head requirements at low rates of waterflow and maximize pumped pumpwater flow at higher water flow rates.Using such pumps in this manner is thus essentially the reverse of theirtypical function in other conventional applications. Instead of beingprovided with constant input power and then delivering a variableoutput, here the pump is provided with variable input power and isoperated to deliver an essentially constant output pressure over as muchof a range as is practical to obtain. The pumping system can be combinedwith a hydro plant and water storage system to provide firm power to thelocal grid. Use of such variable displacement piston pumps is aneffective, cost-efficient way to harness intermittent tidal energy andbalance it into continuous firm power.

A preferred pump for this application is a variable displacement axialpiston pump designed for use at low RPM and comprises a central inboardrotating swash plate pivot assembly with fixed outboard piston cylinderclusters and associated hardware. The pump may desirably be designed tooperate with greater maximum swash plate angles than is typical inconventional axial piston pumps. Further, the pump can be optionallydesigned to pump in either rotation direction to accommodate a reversalin direction of the driving water flow.

Generally, a hydropower pump intended for such applications comprises avariable displacement piston pump comprising a rotating shaft, a pistoncylinder cluster, a manifold and valve assembly, a piston assembly, aswash plate pivot assembly, and a control assembly for adjusting theangle of the swash plates in the swash plate pivot assembly. Thehydropower pump further comprises a waterwheel blade connected to theouter casing and rotating shaft. In one suitable embodiment, thevariable displacement piston pump in the hydropower pump is theaforementioned variable displacement axial piston pump.

A hydroelectric power system for generating tidal power can thuscomprise the aforementioned hydropower pump and a pier comprising thehydropower pump which is anchored to a seabed location to orient thewaterwheel blade with respect to the tide. The system further comprisesan upper reservoir for accumulating pumpwater pumped by the hydropowerpump, a hydro turbine for generating electrical power, a lower reservoirfor accumulating pumpwater passing through the hydro turbine, a penstockfor piping pumpwater from the hydropower pump to the upper reservoir andfor piping pumpwater from hydropower pump and from the upper reservoirthrough the hydro turbine and to the lower reservoir, and a pipingnetwork for returning pumpwater from the lower reservoir to an inlet ofthe hydropower pump and for providing pumpwater from an outlet of thehydropower pump to the penstock, and a controller for controlling thecontrol assembly in the hydropower pump.

The disclosure is suitable for generating hydroelectric power fromsources of flowing water in which the water speed varies over aconsiderable range. In general, this is accomplished by providing theaforementioned hydropower pump, providing a supply of pumpwater,positioning the waterwheel blade in the flowing water such that the pumpshaft rotates with the flow of water and pumps pumpwater from thesupply, and controlling the angle of the swash plates in the pump suchthat the angle is decreased and increased in accordance with arespective decrease and increase in water speed while maintaining anessentially constant output pressure of pumpwater from the pump overmost of the water speed range (output pressure can be maintainedessentially constant except for water speeds near zero). A portion ofthe pumped pumpwater is stored in an upper reservoir positioned abovethe hydropower pump.

There are several design options for variable displacement piston pumpswhich may be considered for this application. However, an axial pistonpump design with outboard or external swash plates and with the intakeand discharge at the centre of the pump body would require means forgetting intake and discharge flow lines through rotating mechanisms. Apump design with outboard swash plate and inboard piston cylinderclusters could be considered in which the waterwheel was mountedexternally on either end of the pump shaft, but this could undesirablyresult in an extremely wide machine. And pumps with rotating pistoncylinder clusters and fixed swash plates may be contemplated buttypically these have been designed to operate in oil to lubricate thecomponents and would thus be difficult to adapt for pumping water.Variations of shaft-driven variable stroke axial piston pumps orvariable stroke radial piston pumps could be adapted for use and mountedseparately on either end of the drive rotors' axle shaft, but may not benearly as simple or compact.

A variable displacement axial piston pump that is particularly suitablefor this application comprises a housing frame comprising a rotatingouter core, and a rotating shaft within the housing frame and connectedto the outer core in which the shaft defines an axis of rotation for thepump. The pump further comprises a fixed outboard piston cylindercluster at an end of the shaft (and preferably each end of the shaft)within the housing frame in which each cylinder cluster comprises atleast one piston cylinder. The pump also comprises a fixed manifold andvalve assembly connected to the outboard head of each fixed outboardpiston cylinder cluster. The manifold and valve assembly may be adjacentto the outboard head or alternatively may be connected thereto from aremote location. Also, the pump comprises a piston assembly at the endor ends of the shaft at the inboard opening of each piston cylindercluster and each piston assembly comprises at least one piston, a pistonrod connected to the piston, and a piston rod mounting assembly in whicheach piston assembly is mounted such that each piston is capable ofreciprocating axial movement within its adjacent piston cylinder and thepiston rod mounting assembly is capable of pivoting with respect to theshaft. The pump also comprises a rotating swash plate pivot assemblycomprising a pivoting swash plate subassembly at each end of the shaftinboard of each piston assembly and connected to the shaft so as torotate with the shaft and be capable of pivoting with respect to theshaft, and a swash plate adjustment subassembly connected to eachpivoting swash plate subassembly and mounted to cause each swash platesubassembly to pivot according to adjustment of the swash plateadjustment subassembly (e.g. length change of the swash plate adjustmentsubassembly). Finally, the pump comprises a control system forcontrolling the length of the swash plate adjustment subassembly andhence the angle of the swash plates.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 shows an exemplary hydroelectric power system of the disclosure.

FIG. 2 shows a view of the subassembly comprising the hydropower pumpand floating barge.

FIG. 3a shows a sketch of the internal workings of a variabledisplacement, axial piston pump for hydroelectric power generation.

FIG. 3b shows an external view of the pump absent rotating outer coreand attached waterwheel.

FIG. 3c shows an exploded view of a portion of the pump.

FIG. 3d shows an exploded view of the outer core and an optionalembodiment for the waterwheel used for the pump.

FIG. 3e shows an exploded view of a portion of the rotating swash platepivot assembly in the pump (viewed from the inboard side of theconnecting flange).

FIG. 3f shows an exploded view of a portion of rotating swash platepivot assembly in the pump (viewed from the outboard side of thepivoting swash plate subassembly).

FIG. 4 shows a sketch of the internal workings of an alternativeembodiment of a variable displacement, axial piston pump comprisingdouble-acting pistons for hydroelectric power generation.

DETAILED DESCRIPTION

Certain terminology is used in the present description and is intendedto be interpreted according to the definitions provided below. Inaddition, terms such as “a” and “comprises” are to be taken asopen-ended. Further, all US patent publications and other patent andnon-patent references cited herein are intended to be incorporated byreference in their entirety.

Herein, the term “about” in quantitative contexts is to be construed asmeaning plus or minus 10%.

The hydroelectric power system of the disclosure is particularly suitedto harness shoreline tidal or other hydro energy available in waterflows characterized by considerably variable flow rates. The systemcomprises a variable displacement piston pump which is operated so as toprovide an essentially constant output pumping pressure and variableoutput volume over most of the range of available water flow rates.(Essentially constant output pumping pressure can be maintained exceptat water speeds near zero.) Desirably, the system provides firm poweroutput throughout the tidal slacks occurring during the tidal reversals.

An exemplary hydroelectric power system is shown in the schematic ofFIG. 1. Hydroelectric power system 1 comprises hydropower pump 2 whichitself comprises variable displacement axial piston pump 3 andwaterwheel blade 4 attached to the rotating shaft (not shown in thisfigure) of axial piston pump 3.

In the embodiment of FIG. 1, hydropower pump 2 is mounted on floatingbarge 5. In turn, the subassembly comprising hydropower pump 2 and barge5 is mounted on pier 6 which is anchored to a seabed location 7 suitablefor power generation. Further, the subassembly is mounted on pier 6 suchthat it is capable of vertical motion and can thus rise and fall withthe tide. In this way, the depth of waterwheel blade 4 in the sea 8 canbe kept essentially constant. Pier 6 is anchored in such a manner so asto orient waterwheel blade 4 optimally with respect to the motion of thetide.

As water flows under hydropower pump 2 with the rise and fall of thetide, waterwheel blade 4 drives axial piston pump 3 which in turn pumpspumpwater received at axial piston pump inlet 9 from lower reservoir 12(sump) out from axial piston pump outlet 10 to penstock 13.

FIG. 2 shows a more detailed view of the subassembly comprisinghydropower pump 2 and floating barge 5.

Hydroelectric power system 1 additionally comprises upper reservoir 14for accumulating pumpwater pumped by hydropower pump 2. Upper reservoir14 is positioned at a suitable elevated location somewhere on land 15.Hydro turbine 16 is used to generate electrical power from pumpwaterprovided from penstock 13.

Penstock 13 pipes pumpwater from hydropower pump 2 to upper reservoir 14for storage during periods of relatively high tidal flow or generallyduring periods where the supply of pumped pumpwater exceeds demand fromhydro turbine 16. Penstock 13 also pipes pumpwater directly fromhydropower pump 2 and/or from upper reservoir 14 to hydro turbine 16 inaccordance with electrical demand and in accordance with the supply ofpumpwater available from hydropower pump 2 at any given time.

After passing through hydro turbine 16, pumpwater is returned to lowerreservoir 12 and is thus available again as a supply of pumpwater forhydropower pump 2. Hydroelectric power system 1 comprises a pipingnetwork (not called out in FIG. 1) for returning this pumpwater to inlet9 of axial piston pump 3 and for providing pumpwater from outlet 10 topenstock 13.

System 1 thus employs a relatively closed circuit subsystem for handlingpumpwater and thus the supply of pumpwater may only need to be refreshedfrom time to time. Preferably a supply of fresh water is employed forpumpwater as this reduces problems associated with corrosion, marinegrowth, or the like.

As shown in FIG. 1, hydropower pump 2 is mounted permanently on pier 6with access to the nearby shore. Waterwheel 4 can rotate in eitherdirection with the incoming and outgoing tidal flow. Waterwheel 4 shouldbe relatively unaffected by floating driftwood, ice, and minimallyaffected by marine growth. Mounting hydropower pump 2 above thewaterline and with its axis horizontal allows all sensitive components,bearings and equipment to be located out of the seawater, allowing easeof maintenance and long service life. Optionally, the mounting systemfor hydropower pump 2 can be built such that waterwheel 4 can be raisedout of the water completely for maintenance and safety reasons.Alternatively, the waterwheel may be equipped with retractable blades.

Energy from tidal flow is transferred to axial piston pump 3 viarotation of waterwheel 4. Axial piston pump 3 is designed to operate andpump in either rotation direction and does not need to operate at aconstant rpm. Further, axial piston pump 3 can operate at speeds as lowas one revolution per minute and thus extract the maximum amount ofenergy from waterwheel area in flow without the necessity for a speedincrease gearbox.

Axial piston pump 3 is operated so as to maintain a constant outputpressure regardless of the input torque from the waterwheel by adjustingthe stroke and output volume relative to tidal flow speeds throughoutmost of the entire tide cycle. During periods of high tidal flows, thepump stroke can be reduced thereby allowing the waterwheel to freewheelin order to maintain the volumes required to be pumped or alternativelyto shut down the system. During times of high flow velocity in a giventide cycle, the volume of water pumped will typically exceed the volumedemanded from hydro turbine 16. This excess volume will accumulate inupper reservoir 14 and flow back down penstock 13 to hydro turbine 16during periods of slack tide.

A controller (not called out in FIG. 1) is used to control the operationof variable displacement, axial piston pump 3 in this manner. Constantoutput pressure is achieved by varying the pump displacement inaccordance with the tidal flow. And the pump displacement is varied byadjusting the angle of pivoting swash plates therein. As is known tothose in the art, a wide variety of simple electronic or mechanicalsystems may be considered for use as a suitable controller. Inputs forthe controller may include measured factors such as waterwheel speed,swash plate angle, output pressure and so on.

Other design details and operation considerations may generally bespecific to a given site where the power is to be generated and to theamount of electricity demanded. For sites with very limited reservoircapacity, the system's firm power output will be the 24 hour average ofthe volumes pumped throughout the daily tide cycles and based on thedays of the least tidal movement. For sites with larger reservoirpotential the firm capacity will be the average of the annual volumespumped.

Calculated examples are provided below which illustrate additionaldetails of construction and operation for two possible designs and sizesof power plants modeled using tidal flows and characteristics atJuskatla Narrows in British Columbia, Canada. It is expected that thoseskilled in the art will readily be able to adapt the system design andoperation to other sites and electrical power needs. Of course, thetypical stream flow velocities, volumes, and other tide conditions atthe desired identified site need to be determined and considered. Anddesigns, sizing, and location for a waterwheel, variable displacementaxial piston pump, reservoirs, hydro turbine, etc. that are appropriatefor the site conditions must then be determined.

Particular considerations include the design of the mounting arrangementfor the hydropower pump. For instance, as have been used for waterwheelson floating mills historically, the hull design of barge 5 can be usedto concentrate and accelerate tidal water flow between catamaran stylehulls where waterwheel 4 engages the stream. Another significantconsideration is the design of waterwheel 4. As is known in the art, thepaddle design employed in a given situation may have a significanteffect on operating efficiency.

The variable displacement, piston pump employed in the hydroelectricsystem is also an important consideration and design details can have asignificant impact on performance. An axial pump suitable for suchapplications is illustrated in FIGS. 3a to 3f . The pump is ofrelatively simple construction, is relatively compact, operates at lowrpm, and allows for relatively large adjustment of swash plate angle andhence can provide constant output pressures over wide range of waterstream velocities. Because the present pump operates at much lower rpmcompared to conventional axial piston pumps, friction losses may besubstantially reduced. This allows for the maximum swash plate angle tobe increased over the approximate 18 degrees industry standard common inhigh pressure, high speed swash plate pumps. The present pump istherefore able to function more efficiently and effectively over a widerrange of stream speeds. It is expected that such pumps may achieveangles as high as 25 to 30 degrees.

FIG. 3a shows a sketch of the internal workings of one suitableembodiment of a variable displacement, axial piston pump forhydroelectric power generation. Pump 20 comprises main shaft 23 definingthe axis of rotation for the pump. Within the pump housing are two fixedoutboard piston cylinder clusters at each end of shaft 23. Each pistoncylinder cluster comprises at least one piston cylinder and generallymultiple piston cylinders. In the embodiment depicted here, each clustercomprises nine piston cylinders. Connected to the outboard head of eachpiston cylinder cluster 24 and 25 are fixed manifold and valveassemblies 26 and 27 respectively. A pair of piston assemblies 28 and 29are located at each end of shaft 23 at the inboard opening of eachpiston cylinder cluster 24 and 25 respectively. Each piston assemblycomprises a set of pistons, piston rods connected to the pistons, and amounting assembly for the piston rods. In FIG. 3a , the pistons are notvisible. However, portions of piston rods 31 and each piston rodmounting assembly 32 are visible. Piston assemblies 28, 29 are mountedsuch that the pistons are capable of reciprocating axial movement withinits associated piston cylinder. Further, each piston rod mountingassembly 32 is capable of pivoting with respect to shaft 23.

Pump 20 also comprises rotating swash plate pivot assembly 33 whichincludes a pair of pivoting swash plate subassemblies 34 and 35 at eachend of shaft 23 inboard of each piston assembly 28, 29. Pivoting swashplate subassemblies 34 and 35 are connected to shaft 23 (and thus rotatetherewith) and are additionally capable of pivoting with respect to theaxis of shaft 23. Rotating swash plate pivot assembly 33 also comprisesswash plate adjustment subassembly 36 which is connected to eachpivoting swash plate subassembly 34, 35 and mounted so as to cause eachswash plate subassembly 34, 35 to pivot according to the length of swashplate adjustment subassembly 36.

In the embodiment shown in FIG. 3a , swash plate adjustment subassembly36 comprises hydraulic ram cylinders 37 which connect to both pivotingswash plate subassemblies 34 and 35 to connecting flanges 39. The lengthof swash plate adjustment subassembly 36 is varied by hydraulicallyvarying the extension of hydraulic ram cylinders 37. In this embodiment,hydraulic ram cylinders 37 are double acting and thus can be extended orcontracted via hydraulic control. A control system (also not shown) isemployed to control the extension of the hydraulic ram cylinders andhence the length of swash plate adjustment subassembly 36.

An outline of the location of waterwheel 40 is also shown in FIG. 3a inorder to indicate its relative location with respect to pump 20.Waterwheel 40 is directly coupled to shaft 23. Thus, as waterwheel 40rotates about shaft 23, rotating swash plate pivot assembly 33 is alsoforced to rotate and does so freely and independently of pistonassemblies 28, 29. Piston assemblies 28, 29 do not rotate butreciprocating pumping motion for pistons 30 occurs as a result of therotation of rotating swash plate pivot assembly 33.

The swash plate inclination or angle of pivoting swash platesubassemblies 34 and 35 is adjusted using a simple hydraulic controlsystem such that the primary control input is the pump output pressure.At low stream speeds, there is relatively less power available forpumping, and so the swash plate angle is set at a shallow inclination,thus shortening piston stroke, maximizing mechanical advantage, andmaintaining both the required output pressure and some flow to the upperreservoir even at low speed. As stream speed increases, output force(torque) increases, and the swash plate angle can be increased, thusincreasing piston stroke and hence flow of pumpwater. Once the swashplate angle reaches the maximum allowable, the rotational speed ofwaterwheel 40 is allowed to increase relative to stream flow, thusincreasing the pumpwater flow as well. At faster stream flows, once theswash plate angle has reached maximum, waterwheel 40 is allowed to spinfaster but will no longer operate at its maximum potential power outputand efficiency. (It is thus desirable to be able to achieve greaterswash plate angles and thereby obtain the greatest possible efficiencyover a wider range of stream flows.) Further details of the constructionof variable displacement, axial piston pump 20 are shown in FIGS. 3b to3f FIG. 3b shows an external view of pump 20 absent rotating outer core22 and attached waterwheel 40. In addition to features already disclosedin FIG. 3a , FIG. 3b shows housing frame 21 for pump 20 and tie rods 38.Tie rods 38 tie both stationary outboard flanges of the swash platestogether to balance their angle of adjustment. The diameter of swashplates and carrier bearings employed as well as the number anddisplacement of the piston cylinders are directly related to the size ofpump 20. The width and diameter of the waterwheel employed will dictatethe dimensions of the pump's inner mechanisms. Swash plate diameter andcylinder displacement are sized according to the required outputpressure from the pump. Both of these relate to the input power arisingfrom the stream velocities and the specific requirements of theinstallation site. Once swash plate diameter and the width of outer core22 have been established, the remainder of the component dimensions canbe determined.

FIG. 3c shows an exploded view of a portion of pump 20. Pictured thereinis rotating outer core 22 which is centrally located about pump 20 andcoupled to shaft 23. Outer core 22 serves as an inner core for anattached waterwheel (not shown) as well as the protective outer coverfor the internal mechanisms of the pump. It may be constructed in threeseparate sections: a solid core 41 (e.g. a rolled metal cylinder) andtwo flanged end assemblies 42 which are bolted to the outer races ofcarrier, slewing bearings. (Slewing bearings are typically ball orcylindrical roller bearings that can accommodate axial, radial, andmoment loads. They are not mounted on a shaft or in a housing and areinstead bolted to a seating surface.) The two flanged end assemblieswill allow for bearing alignment. Outer core 22 is also fitted with, forinstance, flanges for attaching a waterwheel. Also shown in FIG. 3c areexploded components which may be used in the design of housing frame 21.These include a base, bearing mounts, additional bearings for shaft 23and track runner bearings, and so on. The track runner bearings act astorque stabilizers for the non-rotating, slewing outboard portion of theswash plates that are connected to the piston rods. Such constructionsare well known in the art and the components are not called out in FIG.3c . The outward forces generated in piston compression will becontained within the pump body.

FIG. 3d shows an exploded view of outer core 22 and an optionalembodiment for waterwheel 40. As shown, optional waterwheel 40 comprisesa series of spokes and blades. In operation, the blades would be mountedso as to be immersed in the flowing water at right angles to thedirection of flow.

FIG. 3e shows an exploded view of a portion of rotating swash platepivot assembly 33 from the inboard side of connecting flange 39. Herehydraulic ram cylinders 37 would be attached via a pin to connectingflange 39. The rod ends of hydraulic ram cylinders 37 connect to acorresponding pivoting swash plate subassembly. FIG. 3e also shows ahydraulic rotary manifold 50 which allows hydraulic fluid to accesshydraulic ram cylinders 37 for purposes of controlling swash plateangle.

FIG. 3f shows an exploded view of a portion of rotating swash platepivot assembly 33 from the outboard side of pivoting swash platesubassembly 34. Pivoting swash plate subassembly 34 may comprise outerand inner bearing carriers 51 and 53 respectively which are used tocontain ring-shaped slewing bearing 52. Subassembly 34 is mounted toshaft 23 via pin 54 which allows subassembly 34 to pivot with respect tothe axis of shaft 23. Not shown in FIG. 3f are the hydraulic cylindersattached to adjust the pivot or swash plate angle of subassembly 34.

Shaft 23 may be constructed of steel box tubing fitted internally withsteel pipe and stitch welded together to prevent distortion under load.Shaft 23 can extend the width of the pump, carried by bearings mountedin the centre of housing frame 21 on either end. The bearing spindlesmay be hollow tubing in order to allow access for hydraulic lines andmounting of rotary manifold 50. A centre flange may be provided whichbolts the shaft to rotating outer core 22 and thus provides rotationalforce from outer core 22 to shaft 23.

Hydraulic ram cylinders 37 may be sized to operate at approximately 50percent of their continuous operating pressure when the pump is underfull load conditions.

Piston cylinder clusters 24, 25, manifold valve assemblies 26, 27 andpiston assemblies 28, 29 may be designed and made in various mannersfamiliar to those skilled in the art. For instance, gusseted flanges maybe used to connect the piston connecting rods to the swash plate 32.Track runners may be employed to accommodate the maximum swash plateangle and act as torque stabilizers for the stationary outboard side ofthe piston assemblies. In order to maintain alignment of the pistons intheir associated cylinder barrels, piston skirts are employed.

An alternative embodiment for a variable displacement, axial pumpsuitable for this application is illustrated in FIG. 4. The maindifferences between this embodiment and that shown in FIGS. 3a-3f arethe use of double-acting pistons in the piston cylinder clusters and therelative configuration of the swash plate subassemblies. The use ofdouble-acting pistons allows for the pistons to pumpwater whentravelling in either direction and any leakage can be kept internal tothe pump. The swash plate subassemblies are now tilted the same amountbut in opposite directions in order to better balance the loading in thepump.

More specifically, FIG. 4 shows a variable displacement, axial pump 60which comprises main shaft 61 defining the axis of rotation for thepump. Within the pump housing are two fixed outboard piston cylinderclusters 62, 63 at each end of shaft 61. In FIG. 4, three pistoncylinders are visible in each cluster. Connected to the outboard head ofeach piston cylinder cluster 62 and 63 are fixed manifold and valveassemblies 64 and 65 respectively. (As shown in FIG. 4, the fixedmanifold and valve assemblies are remote and are connected by hoses tothe outboard heads of the piston cylinder clusters.) A pair of pistonassemblies 66 and 67 are located at each end of shaft 61 at the inboardopening of each piston cylinder cluster 62 and 63 respectively. Eachpiston assembly comprises a set of pistons, piston rods connected to thepistons, and a mounting assembly for the piston rods. Two representativepistons 68 and their associated piston rods 69 are identified in dashedoutline in FIG. 4. Piston assemblies 66, 67 are mounted such that thepistons are capable of reciprocating axial movement within itsassociated piston cylinder. As mentioned, here fixed manifold and valveassemblies 64, 65 and piston assemblies 66, 67 are double-acting andthus can pump water as the pistons reciprocate in either directionthrough hoses 72 (which are connected to the piston cylinders on bothsides of the pistons). As before, the piston rod mounting assemblies arecapable of pivoting with respect to shaft 61.

Pump 60 also comprises rotating swash plate pivot assembly 75 whichincludes a pair of pivoting swash plate subassemblies 70 and 71 at eachend of shaft 61 inboard of each piston assembly 66, 67. Pivoting swashplate subassemblies 70 and 71 are connected to shaft 61 and are capableof pivoting with respect to the axis of shaft 61. Rotating swash platepivot assembly 75 also comprises swash plate adjustment subassembly 76which is connected to each pivoting swash plate subassembly 70, 71 andmounted so as to cause each swash plate subassembly 70, 71 to pivotaccording to the length of swash plate adjustment subassembly 76. Asbefore, swash plate adjustment subassembly 76 comprises hydraulic ramcylinder 77 which connects to both pivoting swash plate subassemblies70, 71. The length of swash plate adjustment subassembly 76 is varied byhydraulically varying the extension of hydraulic ram cylinder 77. Againas before, hydraulic ram cylinder 77 is double acting and thus can beextended or contracted via hydraulic control. A control system (againnot shown) is employed to control the extension of the hydraulic ramcylinder and hence the length of swash plate adjustment subassembly 76.

To better balance loading in the embodiment of FIG. 4, swash platesubassemblies 70 and 71 are tilted in equal but opposite directions toone another. Gear segments 78 are mounted to each swash platesubassembly 70, 71 and thus synchronize the tilt between the two.Consequently, hydraulic ram cylinder 77 needs only to be connected tothe swash plate assemblies and does not need to be fixed to anadditional flange.

The following examples are provided to illustrate certain aspects of thedisclosure but should not be construed as limiting in any way.

Examples

Estimated power generation capabilities were determined for ahydroelectric power system based on variable displacement, axial pistonpumps of the disclosure and two possible waterwheel designs when used atMakaii Point in the Juskatla Narrows, on Graham Island of Haida Gwaii,British Columbia, Canada. In this exercise, models were created andevaluated to determine the output capacity of the waterwheels, the flowcapacity of the pumping system, the surface flow velocities in theJuskatla Narrows, and the required pumped water reservoir size and firmpower capacity at the hydroelectric power plant.

In summary, the mean stream flow in the Juskatla Narrows was determinedto be about 1.6 m/s with speeds ranging from zero to 4 m/s. In a firstexample, the selected waterwheel design having a 5 m wheel diameter with2 m wide blades was modeled to produce 3.8 kW in a stream flow of 1.6m/s. When run through the full range of stream flows in the JuskatlaNarrows, the system was estimated to produce a continuous, firm poweroutput of 3.8 kW or more from the hydroelectric power system. In thisexample, it was assumed that an upper storage reservoir was elevated atabout 250 m above sea level and that the hydro turbine was located at apoint just above sea level.

Calculations of the output power capacity of the waterwheel were basedmainly on those presented by Muller et al. in Stream Wheels forApplications in Shallow and Deep Water; Muller, Gerald, S. Denchfield,R. Marth, B. Shelmerdine; 32nd IAHR Conference 2007, Venice, Italy; 01-6Jul. 2007. According to Muller et al., the present waterwheel would bein a deep water situation where the stream bed is substantially deeperthan the submerged depth of the blades and the stream velocity issmaller than critical velocity. The waterwheel's power output is mainlya function of the blade surface area in the water, the stream velocity,and the blade velocity. The forces acting on the blade are a combinationof hydrostatic head differences and momentum exchange from the water tothe blade. The following equations were adapted from Muller et al. Andhere, it was assumed that only one full blade was in the water at anytime. The force F on the blade was determined by:

$F = {{\rho_{w}g{\frac{b}{2}\left\lbrack {\left( {d + {\Delta \; h_{1}}} \right)^{2} - \left( {d + {\Delta \; h_{2}}} \right)^{2}} \right\rbrack}} + {\rho_{w}{b\left( {d + {\Delta \; h_{1}}} \right)}\left( {v_{1} - v_{2}} \right)^{2}}}$

Force F is a combination of the hydrostatic head difference (first termon left hand side) and the momentum exchange (second term on left handside) where ρ_(w) is the water density, g is gravitational force, b isthe width of the blades on the waterwheel. The blade or paddle depthinto the water is given by d, and the water ramp-up height on theupstream portion of the blade is Δh₁ and the drop in water on thedownstream is Δh₂. The free stream velocity is v₁ and the blade velocityis v₂.

The ramp-up water surface on the upstream side of the paddle is givenby:

${\Delta \; h_{1}} = \frac{v_{1}^{2} - v_{2}^{2}}{2g}$

According to Muller the ratio of head difference was determinedexperimentally and is:

${\Delta \; h_{2}} \approx {\frac{2}{3}\Delta \; {h_{1}\left( {{from}\mspace{14mu} {tests}} \right)}}$

The power output P is a function of force and paddle velocity and isgiven by:

P=Fv ₂

From here the torque T from the waterwheel is calculated as:

T=F×r

Using the equations above a power output curve can be drawn based on theblade velocity v₂ at a fixed flow velocity v₁. This power curve wasevaluated experimentally in Muller et al. with a small (0.5 m diameter)waterwheel and compared to calculations using the above equations. Thecalculated power output results were about 85% (at maximum power out) ofthose in the experiment of Muller et al. The difference may be becauseof the assumption here that only one full blade was in the water at anytime whereas in the Muller et al. experiment, multiple blades may havebeen in the water, which would increase the available power.

The waterwheel considered in this first example was 5 m in diameter witha set of rectangular blades that were 2 m wide and equally spaced aroundthe circumference of the waterwheel. FIG. 3d shows a portion of thiswaterwheel design with one of the blades visible. The dip depth of theblade was set to 0.875 m which was based on a ratio of blade depth towheel diameter of 0.175 used in Muller. The recommended range for thedepth is 0.12 to 0.2 of the waterwheel diameter. The number of paddlesor blades was such that at least one full blade must be in the water atany given time. This meant that when one blade was fully extended intothe stream, the next blade was at least touching the water surface. Withthe dimensions selected, calculations indicate an angle of 49.5° betweenblades and hence a minimum number of (7.3 rounded up to) 8 blades forthe prototype model. (Note: the number of blades could be increased andwould thus be expected to increase the power output of the system.)

Using the preceding equations, a theoretical output power curve wascalculated as a function of blade velocity for this specific waterwheelfor a given fixed stream velocity of 1.6 m/s. (This was the mean streamflow rate in Juskatla as discussed below.) Power output was corrected bya factor of 1.15 to account for the increased number of blades in thewaterwheel. From these calculations, a maximum power output of about 3.8kW is obtained when the blade speed is 0.7 to 0.8 m/s or at a ratio ofabout 0.44 to 0.5 times that of the stream velocity. In the Muller etal. experiment, that ratio was about 0.44. Thus, this specificwaterwheel would be expected to produce 3.8 kW in a stream flow of 1.6m/s, but the calculations suggest it can produce 15 kW at 2.5 m/s. Theoutput from an exemplary axial piston pump and finally from thehydroelectric power system overall were then modeled assuming thiswaterwheel power output was available.

The pump model was designed to simulate loading of the waterwheel underdifferent stream speeds. As stream speed increases, causing increasedpower transmission via the water wheel, pump loading on the wheel isincreased by increasing the swash plate angle. Output pressure ismaintained, with the increase in power being used to increase pump flow.The model expressed changes in flow and head with respect to swash plateangle and available torque.

The torque output of the waterwheel under varying stream speeds isconverted to force acting through the swash by:

Torque(Nm)=Force(N)×Swash plate radius(m)

As there are two swash plates driven by the shaft, total force isdivided by two to yield swash plate force per piston block. Swash plateradius is a function of the maximum allowable swash plate angle and theswept stroke of the cylinder. For purposes of this first example, aconventional maximum swash plate angle of 18 degrees was assumed.

Swash plate diameter then is given by:

Swash plate diameter(m)=Cylinder swept stroke(m)÷sin 18°.

The rotating force acting through the swash plate was resolved into areciprocating force using vectors. The swash plate was treated as aninclined plane. It was further assumed that there were no significantfriction losses in the swash plate bearings.

To further simplify the analysis, it was assumed that there would be anet positive suction head for all the cylinders on the intake stroke. Inother words, it was assumed that no energy would be expended drawingwater into the cylinders due to a positive head on the intake side (i.e.that the tail-race reservoir was elevated above the pump.) It wasfurther assumed that at any given time in the cycle of a revolution,that half the cylinders would be on the intake cycle and the other halfwould be on the output cycle. Therefore, at any given time, half thenumber of cylinders will be utilizing the available pumping force. Toaccount for the various dynamic hydraulic friction losses associatedwith one-way valves, restricted exit losses, and pipe friction losses,it was assumed here that a very conservative estimate for these dynamicfriction losses would be a doubling of the maximum static head involved(i.e. here the maximum static head was taken to be 250 m, and thusdynamic friction losses would be equivalent to about 500 m).

For this model, an axial pump similar to that shown in FIGS. 3a-3f wasassumed. The number of pump cylinders, the cylinder dimensions, and theswash plate angle had been configured to optimize pump output at anaverage stream speed of 1.6 m/s. Specifically, these parameters were #pump cylinders=10 (at each end), swept cylinder stroke=30 cm, cylinderbore diameter=12 cm, with calculated swash diameter=97 cm, pistonCSA=0.011 m², and swept volume=0.0034 m³. Then, assuming the volumetricefficiency was a relatively low 80%, the pressures generated in eachcylinder on the output cycle, available pumping head, flow perrevolution, and output volume per unit time could then be calculated asis known to those skilled in the art.

From this model, it was found that torque reaches a maximum of 45 kNmwhen the swash plate angle reaches it maximum of 18 degrees, whichoccurs at stream velocities above 3 m/s. Up to 3 m/s, the maximumavailable power from the hydropower pump is fully used. Above thislimit, the waterwheel will spin at a higher rpm, pumping pumpwater at ahigher rate, but the pump is not using the maximum available power fromthe waterwheel. (Again, providing for greater possible swash plateangles raises this limit and thus allows for an increase in efficiencyat these greater stream velocities.)

From the different stream velocities, power was then calculated using:

Power(W)=head(m)×flow(kg/s)×gravity(m/s²)×turbine efficiency (%)

The pressure head, however, varies depending on the stream velocity ofthe tidal flow. Using the present model, the pressure head varies at theturbine temporarily during periods of tidal slack. When the pump isoperating, the pressure will rise to 500 m head at the turbine nozzle(taking into account dynamic friction losses as mentioned above). Someof the pumped water will go up to the upper reservoir and some will feeddirectly into the hydro plant. When the hydro plant is being fed only bythe upper reservoir the water pressure will be lower, dropping to 250 mof head. For simplicity here, it was assumed that 50% of the watervolume will feed the turbine directly and 50% will flow back from theupper reservoir, and that the average pressure that the nozzleexperiences is midway between these extremes, i.e., 375 m total head.This was used to calculate power. A typical plant efficiency of 0.8 forthe hydro turbine was also assumed since a significant portion of thepumped water goes directly into the hydro plant. With an output powerfrom the waterwheel of approximately 3.8 kW at 1.6 m/s stream velocity,the flow available for the hydroelectric power plant is 0.62 l/s. So,using the preceding equation, power was calculated as:

Power=375 m×0.62 litre(kg)/s×9.8 m/s2×0.8=1.8 kW

Therefore, the expected generated electrical power from thehydroelectric power system is 1.8 kW. This represents a hydroplantefficiency of about 48% (1.8/3.8 kW) at this stream velocity. A detailedtable of parameters and values for the preceding models is provided inTable 1 below.

TABLE 1 Theoretical system performance data versus water speed for 1stexample Stream Paddle Useful Paddle velocity velocity Ratio power forceTorque v1 v2 v2/v1 RPM dh1 dh2 kW kN kNm 0 0.00 0.0 0.000 0.000 0.000.00 0.00 0.1 0.04 0.44 0.2 0.000 0.000 0.00 0.02 0.04 0.2 0.09 0.44 0.30.002 0.001 0.01 0.08 0.16 0.3 0.13 0.44 0.5 0.004 0.002 0.02 0.18 0.370.4 0.18 0.44 0.7 0.007 0.004 0.06 0.32 0.66 0.5 0.22 0.44 0.8 0.0100.007 0.11 0.50 1.03 0.6 0.26 0.44 1.0 0.015 0.010 0.19 0.72 1.48 0.70.31 0.44 1.2 0.020 0.013 0.30 0.98 2.02 0.8 0.35 0.44 1.3 0.026 0.0180.45 1.29 2.65 0.9 0.40 0.44 1.5 0.033 0.022 0.65 1.63 3.37 1 0.44 0.441.7 0.041 0.027 0.89 2.02 4.17 1.1 0.48 0.44 1.8 0.050 0.033 1.19 2.465.07 1.2 0.53 0.44 2.0 0.059 0.039 1.55 2.94 6.06 1.3 0.57 0.44 2.20.070 0.046 1.98 3.47 7.15 L4 0.62 0.44 2.4 0.081 0.054 2.49 4.04 8.341.5 0.66 0.44 2.5 0.093 0.062 3.08 4.67 9.63 1.6 0.70 0.44 2.7 0.1050.070 3.76 5.34 11.02 1.7 0.75 0.44 2.9 0.119 0.079 4.54 6.07 12.52 1.80.79 0.44 3.0 0.133 0.089 5.42 6.85 14.13 1.9 0.84 0.44 3.2 0.149 0.0996.42 7.69 15.85 2 0.88 0.44 3.4 0.165 0.110 7.55 8.58 17.69 2.1 0.920.44 3.5 0.181 0.121 8.81 9.53 19.66 2.2 0.97 0.44 3.7 0.199 0.133 102110.54 21.75 2.3 1.01 0.44 3.9 0.218 0.145 11.76 11.62 23.97 2.4 1.060.44 4.0 0.237 0.158 13.48 12.76 26.32 2.5 1.10 0.44 4.2 0.257 0.17115.37 13.97 28.81 2.6 1.14 0.44 4.4 0.278 0.185 17A4 15.25 31.45 2.71.19 0.44 4.5 0.300 0.200 19.72 16.60 34.24 2.8 1.23 0.44 4.7 0.3230.215 22.21 18.03 37.18 2.9 1.28 0.44 4.9 0.346 0.231 24.92 19.53 40.283 1.32 0.44 5.0 0.370 0.247 27.87 21.11 43.55 3.1 1.43 0.46 5.5 0.3860.257 31.04 21.70 44.75 3.2 1.58 0.49 6.0 0.396 0.264 34.19 21.70 44.753.3 1.72 0.52 6.6 0.405 0.270 37.29 21.70 44.75 3.4 1.86 0.55 7.1 0.4130.276 40.34 21.70 44.75 3.5 2.00 0.57 7.6 0.421 0.281 43.34 21.70 44.753.6 2.13 0.59 8.2 0.429 0.286 46.30 21.70 44.75 3.7 2.27 0.61 8.7 0.4360.291 49.22 21.70 44.75 3.8 2.40 0.63 9.2 0.443 0.295 52.11 21.70 44.753.9 2.53 0.65 9.7 0.449 0.299 54.96 21.70 44.75 4 2.66 0.67 10.2 0.4550.303 57.79 21.70 44.75 Tang. force/ Swash Swept Force Hydro- swashplate volume/ needed/ Maximum Maximum power plate angle cylinder swashflow flow out KN degrees m{circumflex over ( )}3 kN m{circumflex over( )}3/sec cu. ft/sec kW Efficiency 0.0 0 0     0.0 0.00000 0.0000 0.00.02 3.81E−06 0.0 0.00000 0.0000 0.00 0.58 0.2 0.08 1.52E−05 0.2 0.000000.0000 0.00 0.58 0.4 0.16 3.057E−05  0.4 0.00000 0.0001 0.01 0.51 0.70.28 5.33E−05 0.7 0.00001 0.0003 0.03 0.50 1.1 0.44 8.38E−05 1.1 0.000020.0007 0.06 0.50 1.5 0.60 0.000114 1.5 0.00003 0.0011 0.09 0.48 2.1 0.830.000160 2.1 0.00005 0.0018 0.15 0.49 2.7 1.07 0.000206 2.7 0.000070.0026 0.22 0.48 3.5 1.39 0.000267 3.5 0.00011 0.0038 0.32 0.49 4.3 1.710.000327 4.3 0.00015 0.0052 0.43 0.49 5.2 2.07 0.000396 5.2 0.000200.0069 0.57 0.48 6.2 2.46 0.000472 6.2 0.00025 0.0090 0.75 0.48 7.4 2.940.000563 7.4 0.00033 0.0116 0.97 0.49 8.6 3.42 0.000654 8.6 0.000410.0145 1.21 0.49 9.9 3.93 0.000753 9.9 0.00051 0.0179 1.49 0.48 11.34.49 0.000859 11.3 0.00062 0.0217 1.81 0.48 12.9 5.12 0.000980 12.90.00075 0.0264 2.20 0.48 14.6 5.79 0.001108 14.6 0.00089 0.0316 2.630.48 16.3 6.46 0.001236 16.3 0.00105 0.0372 3.10 0.48 18.2 7.21 0.00137918.2 0.00124 0.0436 3.64 0.48 20.2 8.00 0.001528 20.2 0.00144 0.05084.23 0.48 22.4 8.86 0.00169  22.4 0.00167 0.0589 4.91 0.48 24.7 9.760.001862 24.7 0.00192 0.0678 5.65 0.48 27.1 10.70 0.002039 27.1 0.002190.0774 6.45 0.48 29.7 11.71 0.002229 29.7 0.00250 0.0882 7.35 0.48 32.412.76 0.002425 32.4 0.00283 0.0998 8.32 0.48 35.3 13.88 0.002633 35.30.00319 0.1125 9.38 0.48 38.3 15.03 0.00285  38.3 0.00357 0.1261 10.510.47 41.5 16.25 0.003072 41.5 0.00399 0.1410 11.75 0.47 44.9 17.530.003308 44.9 0.00445 0.1570 13.09 0.47 46.1 18.00 0.00339  46.1 0.004940.1746 14.55 0.47 46.1 18.00 0.00339  46.1 0.00545 0.1923 16.03 0.4746.1 18.00 0.00339  46.1 0.00594 0.2097 17.48 0.47 46.1 18.00 0.00339 46.1 0.00642 0.2269 18.91 0.47 46.1 18.00 0.00339  46.1 0.00690 0.243720.31 0.47 46.1 18.00 0.00339  46.1 0.00737 0.2604 21.70 0.47 46.1 18.000.00339  46.1 0.00784 0.2768 23.07 0.47 46.1 18.00 0.00339  46.1 0.008300.2930 24.42 0.47 46.1 18.00 0.00339  46.1 0.00875 0.3091 25.76 0.4746.1 0.00339  46.1 0.00920 0.3250 27.09 0.47

The mean power output of the model over the full range of stream flowvelocities however should vary significantly from the abovecalculations. Stream velocities and mean power output from thehydroelectric power system were thus estimated as follows.

The flow rate of water going in and out of the Juskatla Inlet wasdetermined based on hourly tide data (provided by the CanadianHydrographic Service at Fisheries and Oceans Canada). Mass conservationwas assumed and flow coming in from the surrounding watershed wasassumed to be insignificant compared to the tidal flow. The verticalvelocity of the Juskatla inlet water surface was calculated by takingthe difference in tide height between each hour and dividing by theinterval time. The area of the inlet was estimated at about 35 km². Thecross-sectional area of the Juskatla Narrows was given as 720 m² (as perHart, Stephen, 2008, Haida Gwaii/Queen Charlotte Islands DemonstrationTidal Power Plant Feasibility Study. A Hatch Energy report for BritishColumbia Ministry of Energy, Mines and Petroleum Resources). Thearea-averaged flow velocity in the Narrows was calculated and adjustedusing a constant of 0.83 (determined by matching the calculated flow tothat measured in practice as at Jun. 9, 2011).

From the determined frequency distribution of flow velocities, the mostfrequently occurring water surface velocity was 1.3 m/s and the averagestream flow velocity was 1.6 m/s. The estimated flow velocity rangedfrom 0 to 4 m/s.

Using the preceding output calculations, these tidal velocities werethen converted into pumped flow rate. The hourly pumped volumes ofpumpwater were summed up into daily volume flows. The average flow wasfound to be 0.0013 m³/s and the daily averaged pumped volume was 111 m³to the upper reservoir at 250 m static head. This is the average pumpedflow over the whole range of stream velocities (as opposed to the pumpedflow of 0.62 l/s at 1.6 m/s). The pressure head, however, variesaccording to the phase of tidal flow. When the pump is operating thepressure will rise to 500 m head at the hydro turbine nozzle. Asmentioned, the pressure head varies at the turbine temporarily duringperiods of tidal slack. When the turbine is being operated by thereservoir only, the water pressure drops to 250 m. It was assumed thatthe average pressure that the nozzle experiences is midway between theseextremes or 375 m total head. A typical plant efficiency of 0.8 for thehydro turbine was assumed.

This time then:

Power=375 m×1.3 litre(kg)/s×9.81 m/s²×0.8

And therefore potential electrical power available for generation at thehydro site will be 3.8 kW using the above hydropower pump.

Finally, an estimate for the required reservoir size was made. In thepreceding, the pumped flow ranged from 44 m³ to 220 m³ per day for theexample pump in an average stream flow of 1.6 m/s. The upper reservoirwas taken to start at about 800 m³ of water. It was determined that areservoir holding 1100 m³ of water would be required to accommodate thesystem needs over the course of a year (just becoming completely emptyin October and reaching its maximum in January). No consideration wasgiven to water evaporation or rain accumulation in this estimate.

The preceding model was based on very conservative assumptions forfriction losses and pump capability. In a second example, an axial pumpwith greater maximum swash plate angle and double-acting cylinder designsimilar to that shown in FIG. 4 was assumed. In addition, a morerealistic, lower expectation for friction losses was assumed. Andfinally as listed below, certain other changes in waterwheel design andcylinder parameters were assumed.

Here, the waterwheel design considered was the same as in the previousexample except that the dip depth of the blade was set to 0.800 m whichwas based on a ratio of blade depth to wheel diameter of 0.2. Also, anangle of 53.1° between blades and hence a minimum number of 7 blades(6.8 rounded up) was assumed.

This time, a maximum swash plate angle of 30 degrees was assumed. Andfurther, 8 double-acting piston cylinders were assumed (i.e. 4 at eachend) with the following characteristics: swept cylinder stroke=37.5 cm,cylinder bore diameter=20.3 cm, calculated piston CSA=0.032 m², andswept volume=0.0122 m³.

And finally, more likely realistic friction losses were assumed suchthat a required head of only 286 m was assumed to obtain the same grosshead of 250 m.

A detailed table of parameters and values for this second example isprovided in Table 2 below.

TABLE 2 Theoretical system performance data versus water speed for 2ndexample Stream Paddle Useful Paddle velocity velocity Ratio power forceTorque v1 v2 v2/v1 RPM dh1 dh2 kW kN kNm 0 0.00 0.0 0.000 0.000 0.000.00 0.00 0.1 0.04 0.44 0.2 0.000 0.000 0.00 0.02 0.05 0.2 0.09 0.44 0.30.002 0.001 0.01 0.09 0.18 0.3 0.13 0.44 0.5 0.004 0.002 0.03 0.20 0.410.4 0.18 0.44 0.7 0.007 0.004 0.06 0.36 0.73 0.5 0.22 0.44 0.8 0.0100.007 0.13 0.57 1.14 0.6 0.26 0.44 1.0 0.015 0.010 0.22 0.82 1.64 0.70.31 0.44 1.2 0.020 0.013 0.35 1.12 2.24 0.8 0.35 0.44 1.3 0.026 0.0180.52 1.47 2.93 0.9 0.40 0.44 1.5 0.033 0.022 0.74 1.86 3.73 1 0.44 0.441.7 0.041 0.027 1.02 2.31 4.61 1.1 0.48 0.44 1.8 0.050 0.033 1.36 2.805.60 L2 0.53 0.44 2.0 0.059 0.039 1.77 3.35 6.70 1.3 0.57 0.44 2.2 0.0700.046 2.26 3.95 7.89 1.4 0.62 0.44 2.4 0.081 0.054 2.83 4.60 9.20 1.50.66 0.44 2.5 0.093 0.062 3.50 5.30 10.61 1.6 0.70 0.44 2.7 0.105 0.0704.27 6.07 12.13 1.7 0.75 0.44 2.9 0.119 0.079 5.15 6.89 13.78 1.8 0.790.44 3.0 0.133 0.089 6.15 7.77 15.53 1.9 0.84 0.44 3.2 0.149 0.099 7.288.71 17.42 2 0.88 0.44 3.4 0.165 0.110 8.55 9.71 19.42 2.1 0.92 0.44 3.50.181 0.121 9.96 10.78 21.56 2.2 0.97 0.44 3.7 0.199 0.133 11.53 11.9223.83 2.3 1.01 0.44 3.9 0.218 0.145 13.28 13.12 26.24 2.4 1.06 0.44 4.00.237 0.158 15.20 14.39 28.79 2.5 1.10 0.44 4.2 0.257 0.171 17.32 15.7431.48 2.6 1.14 0.44 4.4 0.278 0.185 19.64 17.16 34.33 2.7 1.19 0.44 4.50.300 0.200 22.18 18.67 37.33 2.8 1.23 0.44 4.7 0.323 0.215 24.95 20.2540.50 2.9 1.28 0.44 4.9 0.346 0.231 27.96 21.91 43.83 3 1.32 0.44 5.00.370 0.247 31.24 23.66 47.33 3.1 1.36 0.44 5.2 0.395 0.264 34.788 25.5051.01 3.2 1.41 0.44 5.4 0.421 0.281 38.63 27.44 54.87 3.3 1.45 0.44 5.50.448 0.299 42.78 29.46 58.92 3.4 1.50 0.44 5.7 0.476 0.317 47.25 31.5963.17 3.5 1.54 0.44 5.9 0.504 0.336 52.07 33.81 67.63 3.6 1.58 0.44 6.10.533 0.355 57.25 36.14 72.29 3.7 1.63 0.44 6.2 0.563 0.375 62.81 38.5877.16 3.8 1.67 0.44 6.4 0.594 0.396 68.77 41.13 82.26 3.9 1.72 0.44 6.60.626 0.417 75.15 43.80 87.59 4 1.76 0.44 6.7 0.658 0.439 81.98 46.5893.16 Tang. force/ Swash Force Swept Hydro- swash plate needed/ volume/Maximum Maximum power plate angle swash cylinder flow flow out KNdegrees kN m{circumflex over ( )}3 m{circumflex over ( )}3/sec cu.ft/sec kW Efficiency 0.0 0.00 0.0 0.00000 0.00000 0.0000 0.0 0.01 0.00.00001 0.00000 0.0000 0.00 0.57 0.2 0.06 0.2 0.00003 0.00000 0.00010.00 0.57 0.4 0.13 0.4 0.00007 0.00001 0.0003 0.02 0.57 0.7 0.24 0.70.00013 0.00002 0.0007 0.04 0.57 1.2 0.37 1.2 0.00020 0.00004 0.00130.07 0.57 1.7 0.53 1.7 0.00029 0.00006 0.0022 0.12 0.57 2.3 0.73 2.30.00040 0.00010 0.0035 0.20 0.57 3.0 0.95 3.0 0.00052 0.00015 0.00530.29 0.57 3.8 1.21 3.8 0.00066 0.00021 0.0076 0.42 0.57 4.8 1.50 4.80.00082 0.00029 0.0104 0.58 0.57 5.8 1.82 5.8 0.00100 0.00039 0.01390.77 0.57 6.9 2.17 6.9 0.00119 0.00051 0.0181 1.01 0.57 8.1 2.56 8.10.00141 0.00066 0.0231 1.29 0.57 9.5 2.98 9.5 0.00164 0.00082 0.02901.61 0.57 10.9 3.44 10.9 0.00189 0.00102 0.0359 1.99 0.57 12.5 3.93 12.50.00216 0.00124 0.0437 2.43 0.57 14.2 4.46 14.2 0.00245 0.00149 0.05272.93 0.57 16.0 5.03 16.0 0.00276 0.00178 0.0629 3.49 0.57 17.9 5.63 17.90.00309 0.00211 0.0743 4.13 0.57 20.0 6.28 20.0 0.00344 0.00247 0.08724.84 0.57 22.2 6.96 22.2 0.00382 0.00287 0.1015 5.64 0.57 24.5 7.69 24.50.00421 0.00332 0.1173 6.52 0.57 27.0 8.45 27.0 0.00463 0.00382 0.13487.49 0.56 29.6 9.26 29.6 0.00507 0.00436 0.1539 8.55 0.56 32.4 10.1132.4 0.00553 0.00495 0.1749 9.72 0.56 35.4 11.00 35.4 0.00601 0.005600.1978 10.99 0.56 38.4 11.94 38.4 0.00651 0.00631 0.2226 12.37 0.56 41.712.92 41.7 0.00704 0.00707 0.2495 13.86 0.56 45.1 13.94 45.1 0.007580.00789 0.2785 15.47 0.55 48.7 15.00 48.7 0.00815 0.00877 0.3096 17.200.55 52.5 16.11 52.5 0.00874 0.00971 0.3430 19.06 0.55 56.5 17.26 56.50.00934 0.01072 0.3786 21.03 0.54 60.7 18.45 60.7 0.00997 0.01179 0.416423.14 0.54 65.1 19.68 65.1 0.01061 0.01293 0.4566 25.37 0.54 69.6 20.9669.6 0.01126 0.01413 0.4990 27.73 0.53 74.4 22.26 74.4 0.01193 0.015400.5437 30.21 0.53 79.5 23.60 79.5 0.01261 0.01673 0.5906 32.82 0.52 84.724.98 84.7 0.01330 0.01812 0.6397 35.55 0.52 90.2 26.38 90.2 0.013990.01957 0.6909 38.39 0.51 95.9 27.81 95.9 0.01469 0.02107 0.7441 41.340.50

The calculated power out is markedly greater for this second example andillustrates the potential for improvement given appropriate waterwheeland pump designs and if friction losses are kept reasonably low.

All of the above mentioned U.S. patents and applications, foreignpatents and applications and non-patent publications referred to in thisspecification, are incorporated herein by reference in their entirety.

While particular embodiments, aspects, and applications of the presentdisclosure have been shown and described, it is understood by thoseskilled in the art, that the disclosure is not limited thereto. Forinstance, the detailed description discussed a hydroelectric systemcomprising a single hydropower pump mounted on a floating barge.Depending on needs and site limitations, multiple hydropower pumps maybe employed in a system. Further, it may be unnecessary in practice tomaintain the hydropower pump at a constant height with respect to themoving stream and thus a floating mount may be unnecessary. Furtherstill, while an axial piston pump like that described above offerscertain advantages, it is possible to use other variable displacementpiston pumps. For instance, a configuration using a vertical axiswaterwheel or turbine and a variable displacement, radial piston pumpmay be considered. In such an embodiment, an advantage is that morediameter is available above the waterline. And further still, withregards to the aforementioned variable displacement, axial piston pump,the swash plate adjustment subassembly may be pneumatically operatedinstead of hydraulically operated and may be adjusted by means of a geardrive, machine screw or other suitable mechanisms. It may also proveuseful to consider employing remote manifold and valve assembliesconnected to outboard heads of the fixed outboard piston cylinderclusters.

Thus, many other modifications or alterations may be made by thoseskilled in the art without departing from the spirit and scope of thepresent disclosure. The disclosure should therefore be construed inaccordance with the following claims.

What is claimed is:
 1. A variable displacement axial piston pumpcomprising: a housing frame comprising a rotating outer core; a rotatingshaft within the housing frame and connected to the outer core, theshaft defining an axis of rotation; a fixed outboard piston cylindercluster at an end of the shaft within the housing frame wherein thepiston cylinder cluster comprises at least one piston cylinder; a fixedmanifold and valve assembly connected to the outboard head of the fixedoutboard piston cylinder cluster; a piston assembly at the end of theshaft at the inboard opening of the piston cylinder cluster, the pistonassembly comprising at least one piston, a piston rod connected to thepiston, and a piston rod mounting assembly wherein the piston assemblyis mounted such that each piston is capable of reciprocating axialmovement within its adjacent piston cylinder and the piston rod mountingassembly is capable of pivoting with respect to the shaft; a rotatingswash plate pivot assembly comprising: a pivoting swash platesubassembly at the end of the shaft inboard of the piston assembly andconnected to the shaft so as to rotate with the shaft and be capable ofpivoting with respect to the shaft; and a swash plate adjustmentsubassembly connected to the pivoting swash plate subassembly andmounted to cause the swash plate subassembly to pivot according toadjustment of the swash plate adjustment subassembly; and a controlsystem for controlling the adjustment of the swash plate adjustmentsubassembly.
 2. The variable displacement axial piston pump of claim 1comprising: a fixed outboard piston cylinder cluster at each end of theshaft within the housing frame and each piston cylinder clustercomprises at least one piston cylinder; a fixed manifold and valveassembly connected to the outboard head of each fixed outboard pistoncylinder cluster; a piston assembly at each end of the shaft at theinboard opening of each piston cylinder cluster each comprising at leastone piston, a piston rod connected to the piston, and a piston rodmounting assembly wherein each piston assembly is mounted such that eachpiston is capable of reciprocating axial movement within its adjacentpiston cylinder and the piston rod mounting assembly is capable ofpivoting with respect to the shaft; and the rotating swash plate pivotassembly comprises: a pivoting swash plate subassembly at each end ofthe shaft inboard of each piston assembly and connected to the shaft soas to rotate with the shaft and be capable of pivoting with respect tothe shaft; and the swash plate adjustment subassembly is connected toeach pivoting swash plate subassembly and mounted to cause each swashplate subassembly to pivot according to adjustment of the swash plateadjustment subassembly.
 3. The variable displacement axial piston pumpof claim 2 wherein the fixed outboard piston cylinder clusters comprisea plurality of piston cylinders.
 4. The variable displacement axialpiston pump of claim 2 wherein the fixed outboard piston cylinderclusters and the fixed manifold and valve assemblies are double acting.5. The variable displacement axial piston pump of claim 2 wherein thepivoting swash plate subassemblies at each end of the shaft areparallel.
 6. The variable displacement axial piston pump of claim 2wherein the pivoting swash plate subassemblies at each end of the shaftare not parallel.
 7. The variable displacement axial piston pump ofclaim 6 wherein the pivoting swash plate subassemblies at each end arepivoted with the same degree of tilt but in opposing directions withrespect to the shaft.
 8. The variable displacement axial piston pump ofclaim 2 wherein the swash plate adjustment subassembly is mounted tocause each swash plate subassembly to pivot according to the length ofthe swash plate adjustment subassembly.
 9. The variable displacementaxial piston pump of claim 2 wherein the swash plate adjustmentsubassembly is selected from the group consisting of a single ramcylinder, a machine screw, and a gear drive.
 10. The variabledisplacement axial piston pump of claim 2 wherein the swash plateadjustment subassembly is hydraulically operated.
 11. The variabledisplacement axial piston pump of claim 2 wherein the pivoting swashplate subassemblies are capable of pivoting more than 18 degrees withrespect to the shaft.
 12. The variable displacement axial piston pump ofclaim 11 wherein the pivoting swash plate subassemblies are capable ofpivoting up to about 30 degrees with respect to the shaft.
 13. Ahydropower pump comprising: a variable displacement piston pumpcomprising a rotating shaft, a piston cylinder cluster, a manifold andvalve assembly, a piston assembly, a swash plate pivot assembly, and acontrol assembly for adjusting the angle of the swash plates in theswash plate pivot assembly; and a waterwheel blade connected to therotating shaft.
 14. A hydropower pump comprising: the variabledisplacement axial piston pump of claim 2; and a waterwheel bladeconnected to the rotating shaft.
 15. A hydroelectric power system forgenerating tidal power comprising: the hydropower pump of claim 13; apier comprising the hydropower pump wherein the pier is anchored to aseabed location to orient the waterwheel blade with respect to the tide;an upper reservoir for accumulating pumpwater pumped by the hydropowerpump; a hydro turbine for generating electrical power; a penstock forpiping pumpwater from the hydropower pump to the upper reservoir and forpiping pumpwater from the hydropower pump and from the upper reservoirthrough the hydro turbine; a piping network for providing pumpwater froman outlet of the hydropower pump to the penstock; and a controller forcontrolling the control assembly in the hydropower pump.
 16. Thehydroelectric power system of claim 15 comprising: a lower reservoir foraccumulating pumpwater passing through the hydro turbine; the penstockis additionally for piping pumpwater from the hydropower pump and fromthe upper reservoir through the hydro turbine and to the lowerreservoir; and the piping network is additionally for returningpumpwater from the lower reservoir to an inlet of the hydropower pump.17. A method for generating hydroelectric power comprising: identifyinga source of flowing water wherein the water speed varies over a rangegreater than about 1 m/s in breadth; providing the hydropower pump ofclaim 13; providing a supply of pumpwater; positioning the waterwheelblade in the flowing water such that the pump shaft rotates with theflow of water and pumps pumpwater from the supply; controlling the angleof the swash plates in the pump such that the angle is decreased andincreased in accordance with a respective decrease and increase in waterspeed while maintaining an essentially constant output pressure ofpumpwater from the pump over most of the water speed range; and storingthe pumped pumpwater in an upper reservoir positioned above thehydropower pump.
 18. The method of claim 17 wherein the pump shaftrotates at speeds in the range from 0 to about 10 rpm.
 19. The method ofclaim 17 wherein the water speed varies over a range up to about 5 m/sin breadth.
 20. The method of claim 17 wherein the mean speed of theflowing water is greater than or equal to 1.6 m/s.
 21. The method ofclaim 17 wherein the source of flowing water is tidal.